Variable stroke reciprocating mechanism



Feb. l2, 1963 w. F. WARD l-:TAL 3,077,159

VARIABLE STROKE RECIPROCATING MECHANISM Filed Feb. 1o, 1961 4 5 sheets-sheet 1 III"- i i INVENTORS 1 2 W/LL/AM E WARD Q HENRY a WARD, JR.

BY @myZ/SM ATTORNEY Feb. 12, 1963 w. F. WARD ETAL 3,077,159

VARIABLE STROKE RECIPROCATING MECHANISM Filed Feb. l0, 1961 f 5 Sheets-Sheet 2 W W /os (Q /Zl/ l IIIIIIIIIIII INVENTORS Q Humm W/LL/AM f.- WARD N HENRY o. WARD, ./f?.

ATTORNEY Feb. 12, 1963 w. F. WARD ETAL VARIABLE STROKE RECIPROCATING MECHANISM Filed Feb. l0. 1961 5 Sheets-Sheet 3 INV ENTORS WILL/AM E WARD B 4HENRY D. WVRD', JR.

Feb. 12, 1963 w. F. WARD ETAL. 3,077,159

VARIABLE STROKE RECIPROCATING MECHANISM Filed Feb. 10, 1961 5 Sheets-Sheet 4.v

FIG. 8A.

FIG. 7A. 50 Rr/AL smoke ssrn/vs vosmo/ 5 serr//vs INV ENTORS 95 WILL/AM E WARD HENRY D. WARD, JR.

ATTORNEY v Feb. 12, 1963 w. F. WARD ETAL 3,077,159

VARIABLE STROKE RECIPROCATING MECHANISM Filed Feb. 10, 1961 5 Sheets-Sheet 5 FIG. .9A

F ULL-STROKE SETTING F/G. 9B.

INVENTORS WILL/AM E WARD HENRY D. WARD, JR.

BY am@ ym ATTORNEY United States Patent O 3,077,159 VARIABLE STROKE YRECPRQCATING MECHANISM William F. Ward, Lutherville, and Henry D. Ward, Jr.,

Timonium, Md., assignors, by mesne assignments, to

Samuel M. Langston Company, Camden, NJ., a corporation of New .lersey Filed Feb. 10, 1961, Ser. No. 88,332 9 Claims. V(Cl. 101--349) This invention relates generally to printing machinery, and specifically to a mechanism for reciprocating inking rollers in a printing press and a means for varying the ylength of the stroke of the inking rollers.

It is an object of this invention `to provide a mechanism for reciprocating inking rollers in a printing press and for varying the length of stroke of the inking roller.

Still :another object of this invention is to provide a variable stroke reciprocating mechanism for use with inking rollers in printing machinery.

And still another object of this invention is to provide a unique variable stroke reciprocating mechanism which lis economical to manufacture, eiiicient, and reliable in `operational use, and which is easy to install and maintain.

These objects and Vother objects and advantages of this invention will become more apparent from the following detailed specication and accompanying `drawings in which:

FIG. l is an axial section through a roller reciprocating mechanism incorporating features 'of `the invention and is taken along line 1-1 of FIG. 2;

FIG. 2 is a vertical cross section taken along Iline 2-2 of FIG. 1;

FIG. 3 is a horizontal section .taken along line 3 3 of FIG. 1;

FIG. 4 is a fragmentary horizontal section, somewhat similar to FIG. 3, on an enlarged scale and is taken along line 4--4 of FIG. 1;

FIG. 5 is a further horizontal section taken along line 5 5 of FIG. l;

FIG. 6 is a detail perspective of one of the structural elements of the variable stroke reciprocating mechanism;

FIGS. 7A through 7D are schematic views illustrating the cycle of operation of the variable stroke reciprocating mechanism when adjusted to a no-stroke setting;

FIGS. 8A through 8E are schematic views illustrating the cycle of operation of the variable stroke reciprocating mechanism when adjusted to a partial-stroke setting; and

FIGS. 9A through 9D are further schematic views illustrating the cycle of operation of the Variable stroke reciprocating mechanism When adjusted to a full-stroke setting.

Referring now to FIGS. 1 through 6 of the drawings, the variable stroke reciprocating mechanism 10 consists basically of a gearing arrangement `12, which is suspended by means of a main bracket 14 from a printing press side frame 16 so as to receive rotational drive from a driven inking roller 18.

The gearing arrangement 12 translates the rotational drive to a linear motion which is re-applied to the driven roller 18 and to an idler inking roller 20 so as to reciprocate -both rollers 18 and 20 along their axes for the well known purpose of distributing ink as will now be explained.

The inking roller 18, which is remotely driven, is journalled in a roller bearing 22, which is secured in a sideframe 16 by retaining rings 24 and 26. A gear 28 is secured near the shown end of inking roller 18, which meshes and drives a broad faced gear 30.

The gear 30 is fixed to a short shaft 32, the left end of which is journalled in a bearing 34 located in a bearing boss 36 formed in a mounting plate 38' of a main ICC bracket 14, shown best in FIG. 5. Approximately midway of its ends, the shaft 32 is journalled in a second bearing `4t) which is carried by a cantilever boss 42 suspended from the end of an arm 44 which is formed in tegrally with and extends outwardly from the mounting plate 38.

A multiple pitch wor-m 46 is keyed to the right hand end of the shaft 32, and it drives a wormv gear 48. The worm gear 48 is secured to a short, comparatively large diameter shaft 50 whose upper and lower ends are journalled by bearings 52 carried by the spaced upper and lower cantilever bosses 54 formed at the outer end of arm 44. The bearings 52 are restrained against axial movement by at rings 56.

The shaft 50 is provided with a pair of eccentrically arranged parallel -bores 58 and 60 spaced substantially 90 apart as best viewed in FIG. 5. Each of the bores 58 and 6i) receives a shaft 62 and 64, respectively, journalled in spaced Vbearings 66.

Shaft 62 is provided at its lower end with :a gear 68 which walks around within a lower ring gear 70 when the shaft S0 is rotated and similarly the shaft 64 is provided at its upper end with a gear 72 which walks around Within an upper ring gear 74. The ring gears 70 and 74 :are received in close fitting counterbores 76 :and 78, respectively, which are provided in bosses 54. Ring gears '70 and 74 are secured against axial movement -by retainer rings 80 and 82, respectively.

Shaft 62 is provided at its lower end, adjacent gear 68, with `a flange 84 whose outer surface is provided with an eccentric drive boss S6 which carries a roller 88. Similarly, shaft 64 is Vprovided at its upper end, adjacent gear 72, with a flange 9G whose outer surface is provided with an eccentric drive boss 92 which carries :a roller 94.

It should be noted that drive bosses 86 and 92 `are located so that their respective axes directly ioverlie the pitch diameters of their respectively adjacent gears 68 and 72 so that a plane on which lies the axis of boss 86 will lbe tangent to the pitch diameter of the gear 68 and similarly a plane on which lies the axis of boss 92 will be tangent to the pitch `diameter of gear 72. This can best be illustrated at lines A in FIGS. l and 2, at point B in FIG. 4, and in FIGS. 7A through 9D.

It is well known that when the pitch diameter of a gear is exactly half the pitch diameter of a ring gear in which it is travelling, then any given point on the pitch diameter of the inner gear will ltraverse a straight line. The pitch `diameter of the gears 68 and '72 is exactly half the pitch diameter of the ring gears 70 and 74; consequently, the axes of drive bosses 86 and 92 will move along a straight line when gears 63 and 72 are caused to walk around in ring gears 7i) and 74, respectively, when worm gear 48 is rotated.

Rollers 88 and 94 each are located within an elongated slot 96 provided in a pair of drive yokes 98. The left end of each drive yoke 98 is secured through the bearings 100, retainer rings 102, and locknuts 104 to its associated ink roller 18 or 20 so as to reciprocate the ink rollers 18 and 2i) axially without restricting their rotation.

In order to prevent any misalignment of the yokes 98 as they are driven by their respective rollers 88 and 94, a pair of guide bosses 106 are arranged on each yoke 98 so as to travel along one of the pair of cantilever guide rods 168. The guide rods 108 are secured in bosses 110 on the mounting plate 38.

Before proceeding with a `discussion of the principles illustrated in FIGS. 7A through 9D, it should be pointed out `that for purposes of simplicity and clarity only those reference numerals assigned to the upper gearing elements, as viewed in FIGS. 1 and 2, shall be used. However, the same principles apply to the lower gearing elements.

It will be clearly seen from an examination of FIGS. 7A through 9D that the length of stroke of drive yoke 98 depends entirely upon the relative positioning of the drive boss 92 and the roller 94 with respect to the point of contact or mesh between inner gear 72 and the ring gear 74. The figures are arranged in three groups, namely FIGS. 7A through 7D which illustrate a full cycle of operation with the variable stroke reciprocating mechanism set for no stroke; FIGS. 8A through 8E illustrating a full cycle at a partial-stroke setting of the variable stroke reciprocating mechanism y10; and FIGS. 9A through 9D illustrating a cycle of operation with the variable stroke reciprocating mechanism 10 set for full-stroke operation.

The first figure of each group, namely FIGS. 7A, 8A, and 9A, shows shaft 64 and its gear 72 in the same relative position with respect to the ring gear '74. However, the positions of roller 94 differ. In FIG. 7A, roller 94 is shown 180 away from the point of mesh between the gear 72 and lthe ring gear 74.

Following FIGS. 7A through 7D, it will be noted that clockwise rotation of the shaft 50 will drive gear 72 counterclockwise around ring gear 74 causing roller 94 to move along a vertical path in slot 96, thus allowing drive yoke 98 to remain stationary.

In FIG. 8A, roller 94 is positioned 90 away from the point of mesh between the gear 72 and the ring gear '74. As noted from FIGS. 8B through 8E, clockwise rotation of shaft 50 will drive gear 72 counterclockwise, thereby causing the roller 94 to move -in a straight diagonal path from the lower right to the upper left thus driving the guide yoke 98 through a shortened stroke.

In FIG. 9A, the axis of the roller 94 is shown directly over the point of mesh of the gear 72 and the ring gear 74. By following FIGS. 9A through 9D, it will be noted that clockwise rotation of shaft 50 will drive the gear 72 counterclockwise, thus causing the roller 94 to traverse a straight horizontal path, thereby driving the guide yoke 98 through a full stroke.

The repositioning of the rollers 94 and 88, to allow a variety of stroke lengths, is achieved simply and in novel fashion by means of a pair of manually rotatable pinions 112 provided on the inner ends of shafts 114 located in housing i116 which are secured to an outer cover case 118. Pinions y112 engage gear teeth 120 formed around the outer periphery of ring gears 70 and 74. Manual rotation of the shaft 114 Will cause the pinion 112 to rotate ring gears '70 or 74 as well as inner gears 68 or 72, thus repositioning rollers 38 or 94 and changing the stroke of the drive yokes 98.

Housings 116 are formed at their outer ends in a conventional split clamp arrangement 122 so as to lock the shaft 114, by means of a bolt 124, against rotation upon completion of stroke adjustment.

It should be further noted that ring gears 70 and 74 may be separately adjusted, while the printing press is stationary or in operation, foi different length strokes. That is, one inking roller 18 or 20 may be set for full stroke and the second ink roller for no stroke, if so desired.

It should be further noted that as shown best in FIGS. 1, 2, and 5, shafts 62 and 64 are positioned approximately 90 apart. This is an arbitrary arrangement which keeps the reciprocation of the inking rollers 18 and 20 90 out of phase. The bores 58 and 60 could be drilled 180 apart to keep rollers 18 and 20 180 out of phase or, if desirable, gears 68 and 72 could conceivably be installed on opposite ends `of a single shaft, say shaft 62, thereby reciprocating rollers 18 and Z0 in phase.

Obviously many modifications and variations of the present invention are possible in light of the above teachings. It is, therefore, to be understood than within the scope of the appended claims the invention may be practiced otherwise than as specifically described.

What is claimed is:

1. In combination, a ,driving roller, a first shaft positioned substantially perpendicular to the longitudinal axis of said driving `roller, said first shaft having at least one eccentrically arranged longitudinal bore, gear means to impart rotational motion yof said driving roller to said first shaft, a second shaft rotatably secured in each said bore in said first shaft, a ring gear mounted adjacent an end of each said second shaft, a walking gear mounted on each said second shaft and adapted to traverse its respective ring gear upon rotation of said first shaft, au idler roller, means including a drive boss mounted on each said walking gear, the motion of each drive boss being essentially planar, yoke means rotatably connected with said driving roller and said idler roller and adapted to receive each drive boss, whereby the essentially planar motion of each drive boss is translated into reciprocatory motion of said driving roller and said idler roller.

2. The combination of claim l, wherein said gear means to impart rotational motion of said driving roller to said first shaft, comprises, a driving gear secured to said driving roller, a first worm gear secured to said rst shaft, a broad faced gear in engagement with said driving gear, said engagement being retained during reciprocation of said driving roller and said reciprocating roller, and a second worm gear driven by said broad faced gear and coacting with said first worm gear.

3. The combination of claim l, wherein two eccentrically arranged longitudinal bores are provided in said first shaft and hence two second shafts are provided and a ring gear is mounted adjacent an opposite end of each said second shaft.

4. The combination of claim 3, wherein said two eccentrically arranged longitudinal bores are located about from each other.

5. The combination of claim 3, wherein said two eccentrically arranged longitudinal bores vare located about from each other.

6. In combination, a driving roller, a fixed support, means including a first shaft rotatably secured in said fixed support and positioned thereby substantially perpendicular to the longitudinal axis of said driving roller, said first shaft having at least one eccentrically arranged longitudinal bore, means including a broad faced gear to impart rotational motion of said driving roller to said first shaft, a second shaft rotatably secured in each said bore in said first shaft, a ring gear mounted adjacent an end of each said second shaft, a walking gear mounted on each said second shaft and ladapted to traverse its respective ring gear upon rotation of said first shaft, each said walking gear having -a iiange mounted thereon, means including a drive boss mounted on each said flange eccentrically with respect to the longitudinal laxis of its respective second shaft, the motion of each drive boss being essentially planar, an idler roller, yoke means rotatably secured to said driving roller and said idler roller and having a transverse slot adapted to receive each drive boss, whereby the essentially planar motion of each drive boss is translated into reciprocatory motion of said driving roller and said idler roller.

7. A mechanism for converting continuous rotary motion of a driving ink distributing roller into simultaneous reciprocation and rotation thereof and an idler ink distributing roller, comprising, a first shaft positioned substantially perpendicular to the longitudinal axis of said driving ink distributing roller, said first shaft having at least one eccentrically arranged longitudinal bore, means including a broad faced gear to translate rotary motion of said driving ink distributing roller into rotary motion of said first shaft, a second shaft rotatably secured in each said bore in said first shaft, a ring gear mounted adjacent an end -of each said second shaft, a walking gear mounted on each said second shaft and adapted to traverse its respective ring gear upon rotation of said first shaft, an eccentric boss means mounted on each said walking gear, the motion of each boss means being essentially planar, yoke means rotatably connected to said driving and said idler ink distributing rollers and having a traverse slot adapted to receive each boss means, whereby the essentially planar motion of each boss means as supplied by rotation of said driving ink distributing roller and said rst shaft is translated into reciprocatory motion of said driving and said idler ink distributing rollers.

8. A mechanism for converting continuous rotary m0- tion of a driving ink distributing roller into simultaneous reciprocation and rotation thereof and an idler ink distributing roller, comprising, a fixed support, means including a first shaft rotatably secured in said xed support and positioned thereby `substantially perpendicular to the longitudinal axis of said driving ink distributing roller, said irst shaft having a pair of eccentrically arranged longitudinal bores, means including a broad faced gear to translate rotary motion of said driving ink distributing roller into rotary motion of said first shaft, a pair of second shafts rotatably secured in said pair of eccentrically arranged longitudinal bores, respectively, a pair of ring gears mounted adjacent opposite ends of said pair of second shafts, a walking gear mounted on each second shaft and adapted to traverse its respective ring gear upon rotation of said first shaft, an eccentric boss means mounted ou each said walking gear, the motion of each boss means being essentially planar, a pair of yoke means rotatably connected to said driving and Said idler ink distributing rollers, respectively, each yoke means of said pair having a transverse slot adapted to receive its respective boss means, whereby the essentially planar motion of each boss means as supplied by rotation of said driving ink distributing roller and said first shaft into reciprocatory motion of said driving and said idler ink distributing rollers.

9. The mechanism of claim 8 and in addition means to independently rotate each ring gear of said pair to independently change the distance between the axis of each eccentric boss means and the longitudinal axis of said first shaft, whereby the amplitude of reciprocation of said driving and said idler ink distributing rollers is separately variable and controllable.

References Cited in the tile of this patent UNITED STATES PATENTS 1,408,439 Buckminster Mar. 7, 1922 2,155,354 Avery Apr. 18, 1939 2,700,335 Stobb Jan, 25, 1955 2,903,966 Faeber Sept. 15, 1959 2,915,008 Harless et al Dec. 1, 1959 FOREIGN PATENTS 486,889 Germany i Nov. 27, 1929 140,751 Australia Apr. 10, 1951 

1. IN COMBINATION, A DRIVING ROLLER, A FIRST SHAFT POSITIONED SUBSTANTIALLY PERPENDICULAR TO THE LONGITUDINAL AXIS OF SAID DRIVING ROLLER, SAID FIRST SHAFT HAVING AT LEAST ONE ECCENTRICALLY ARRANGED LONGITUDINAL BORE, GEAR MEANS TO IMPART ROTATIONAL MOTION OF SAID DRIVING ROLLER TO SAID FIRST SHAFT, A SECOND SHAFT ROTATABLY SECURED IN EACH SAID BORE IN SAID FIRST SHAFT, A RING GEAR MOUNTED ADJACENT AN END OF EACH SAID SECOND SHAFT, A WALKING GEAR MOUNTED ON EACH SAID SECOND SHAFT AND ADAPTED TO TRAVERSE ITS RESPECTIVE RING GEAR UPON ROTATION OF SAID FIRST SHAFT, AN IDLER ROLLER, MEANS INCLUDING A DRIVE BOSS MOUNTED ON EACH SAID WALKING GEAR, THE MOTION OF EACH DRIVE BOSS BEING ESSENTIALLY PLANAR, YOKE MEANS ROTATABLY CONNECTED WITH SAID DRIVING ROLLER AND SAID IDLER ROLLER AND ADAPTED TO RECEIVE EACH DRIVE BOSS, WHEREBY THE ESSENTIALLY PLANAR MOTION OF EACH DRIVE BOSS IS TRANSLATED INTO RECIPROCATORY MOTION OF SAID DRIVING ROLLER AND SAID IDLER ROLLER. 